Power brake control valve



Dec. 29, 1964 1 D, sco-r1' PowER BRAKE CONTROL VALVE Voriginal Filed Nov. 30. 1961 INVENroR. B/YOHN D. SCOTT ATTORNEY United States Patent 3,163,607 PGWER BRAKE CNTRGL VALVE John D. Scott, South -end, 1nd., assigner to 'he Bendix Corporau'on, South Bend, Ind., a corporation of Delaware Continuation of application Ser. No. 156,115, Nov. 30, 1961. This application Jan. 4, 1963, Ser. No. 249,523 3 Claims. (Cl. 6il--54 .5}

The present invention relates to a fluid pressure control valve whose control member can not only modulate a pressure fluid flow therethrough, but can physically displace :duid to its output port; and more particularly to a power brake control valve incorporating these features. This application is a continuation of US. application Serial No. 156,115.

An object of the present invention is the provision of a new and improved pressure modulating valve of the above mentioned type which is simple iu design, rugged in its construction, and inexpensive to manufacture.

Another object of the present invention is the provision of a new and improved master cylinder of the above mentioned type having a fluid displacement chamber whose outer end is closed olf by means of a valve control member which modulates a pressure flow therethrough, upon a slight inward movement; and which on further inward movement of the control member, causes it to abut an annular piston to cause it to displace fluid from the inner end vof the fluid displacement chamber.

A still further object of the present invention is the provision of a new and improved hydraulic control valve having a iluid displacement chamber into which the valves control member projects, and into which the output pressure of the control valve is communicated to provide a reaction pressure against the control memberthe control valve further including an annular piston abutted by the control member during further inward movement to produce a manual displacement of uid from the control valve structure.

The invention resides in certain constructions, and combinations, and arrangements of parts; and further objects and advantages of the present invention will become apparent to those skilled in the art to which it relates from the following description of the preferred embodiment described with reference to the accompanying drawing forming a part of the specification, and in which:-

- The solitary figure of the drawing schematically illustrates an automotive hydraulic braking system which incorporates a power operated master cylinder embodying principles of the present invention, and which is shown in cross section.

The hydraulic power braking system shown in the drawing generally comprises a gear pump 10 which receives fluid from a low pressure reservoir 12, and discharges the same through a check valve 14 to an accumulator 16. The pressure in the accumulator 16 is maintained within predetermined pressure limits by means of a charging valve 18 which, after the pressure in accumulator 16 reaches a predetermined pressure, unloads the pump 10 through the interconnecting lines Ztl and 22 to the reservoir 12. A pressure sensing line 24 communicates pressure from the accumulator 1d to the charging valve 18 to control the operation of the charging valve. When the pressure in accumulator 16 falls below a predetermined lower limit, the charging valve 18 closes off communication from the pump 1t) to the reservoir 12 through the interconnecting lines 20 and 22 so that the discharge from the pump 1l) flows through the check valve 14 to build up pressure in the accumulator 16.

The hydraulic braking system shown in the drawing further includes a plurality of foundation brakes 26 only CIce one of each of which are actuated by means of a hydraulic wheel cylinder 2S. Actuation of the brakes 26 is produced by communicating pressure to the wheel cylinders 2S to force pistons in their opposite ends, outwardly to in turn force the brake shoes 3th in engagement with the revolving brake drum 32. Pressure from the accumulator 16 is modulated and delivered to the wheel cylinders 26 to produce and control a brake actuation by means of the pressure regulating Valve A about to be described.

The pressure regulating valve A generally comprises a housing 36 having a forwardly and rearwardly extending iluid displacement chamber 38 therein. The rear end of the fluid displacement chamber 38 is closed off by means of .a control member 4t) having suitable seals with respect to the sidewalls of the fluid displacement chamber; and the forward end of the displacement chamber 38 is suitably closed oft by an end wall 46 to provide a fluid pressurizing chamber 48 between the wall 46 and the forward end of the control member 40. The

viluid pressurizing chamber 4S may be sized larger or the control member 4&1 is positioned, and as shown in the drawing is made larger for reasons which will later be apparent. Y

The forward end of the displacement chamber 38 is enlarged or counterbored to provide the pressurizing section d8, and to further provide a shoulder which acts as a stop for limiting rearward motion of an annular piston S2. The shoulder 551 maintains the annular piston 52 forwardly of the control member 40 by an amount which vpermits the normal pressure regulating movement of the control member 40. A suitable seal 54 is provided on the periphery of the annular piston 52 so that it can displace fluid from the pressurizing section 4S. The annular piston 52 is normally held against the shoulder Sil by means of a coil spring 56 positioned between the annular piston 52 and the end wall 46. The control member 40 is biased rearwardly in the displacement chamber 38 by means of a coil spring 58 which is positioned between the end wall 46 and a suitable projection 60 which extends through the central opening 62 of the annular piston 52. A suitable stop or snap ring 6d is provided in the rear end of the chamber 3S to limit rearward movement of the control member di), and

provide the normal retracted position of the control member 4t).

According to principles of the present invention, pressure flow from the accumulator 16 is controlled or modulated to the wheel cylinder 2S. As the control member 40 is moved a small distance forwardly from the normal retracted position shown in the drawings, control member dit is moved forwardly by a ball ended push rod 66; and the construction is such that only approximately a quarter of an inch of forward movement is required of the control member l0 to actuate the brakes when pressure is available in the accumulator 16. As previously indicated, the construction shown in the drawing is provided with an annular fluid displacement piston 52 which can be driven forwardly by the push rod 6d to actuate the brakes manually when insutlicient pressure exists in the accumulator 16. Forward movement of the control member 4d bleeds pressure to the control port 68 of the valve structure, from whence it ilows both to the hydraulic distribution line 34, and interconnecting passages 7d and 72 in the housing 36 to the fluid pressurizing chamber 4S. Pressure in the chamber 43 is of course communicated to the control member 4t) to provide a reaction force which opposes actuating movement of the control rod 66 by an amount which is proportional to the pressure which is being delivered to the wheel cylinders 28. By means of the arrangement shown in thek drawing, one chamber 43 serves both as a reaction chamber for producing a reaction upon the control member 4l), and also as a lluid displacement chamber from which fluid can be displaced manually during a pressure failure in the accumulator 16.

The control valve structure may be of any suitable type,

i as for example, the poppet type, or the slide valve type;

and may be made to communicate pressure to the wheel cylinders 2S and fluid displacement chamber t3 prior to the'time thatthe control member il engages the annular piston 52, or may beL made to engage the annular piston 52 prior to the time thatpressure is communicated to the wheel cylinders 2%, ln the construction shown in the drawing, the exhaust port '7d of the valve structure is positioned rearwardly of the annular piston 52, and is adapted to be closed ol by the control member d@ as the control member du Vmoves forwardly from the retracted position shownr in the drawing. 4Pressure flow to the control port 68 is controlled by the land portion 7o shown by the solid lines in the drawing, and will cause the control port 63 to be opened to pressure prior to the time that the end surface of the control member llt) abuts the annular piston 52. With this arrangement, the brakes are normally operated by pressure from the accumulator 15 without moving the annular piston 52 so that the reaction pressure that opposes valve actuating movement is only that developed by the small forward end of the conf trol member 4l).

-Normal operation of the construction just described therefore is Vinitiated by forward movement of the push rod 6d which causes the forward end of the control member lll to close olf the exhaust port '74, and thereafter communicate pressure from the pressure port 78 to the control port 68 to simultaneously pressurize the wheel cylinders 23 and the fluid pressurizing chamber 43. lnasmuchras the forward end of the control member dll will at this time not have engaged the end of the piston S2, the smaller end of the control member 4l) provides a reaction force which opposes the actuating movement of the control valve structure. lf a lack of pressure exists in accumulator 16, no reaction pressure will be produced to oppose the actuating movement of the control member all so that it sequentially closes the exhaust port 74, opens the control port 68 without actuating the brakes. Thereafter the forward end of the control member lll abuts the annular piston S2 to displace huid out of the fluid displacement chamber 43 to the wheel cylinders 28.

ln order that the pressure generated in the fluid displacement chamber 43 will not `flow backwardly to the ac cumulator, a suitable check valve structure 81B must be provided somewhere between the juncture of the interconnecting passage 7@ and the accumulator lo. This is conveniently accomplished in the embodiment shown in the drawing by means of a seat S2 formed by means of the counterbore in the control ports 68, and a suitable ball valve S4 is biased against the seat by means of a coil spring 36, The coil spring 85 may be held in position in any suitable manner, and as shown in the dra dug, is

l held by means of a conventional tubing ferrule that is used to connect the distribution line Sil-to the housing 3d. A slight amount of leakage may be experienced in the slide valve construction used to close the exhaust port 74; and accordingly, a suitable rubber seal S8 is provided in the end of the control member 4t) to prevent all flou' through the central opening 62 of the annular piston 52, when the end of the control member 40 abuts the annular piston 52 to displace fluid out of the pressurizing chamber 48.

When it is desired to release the annual application of the brakes, rearward movement of the control rod 66 allows the annular piston 52 to be retracted, and thereby reduce the pressure in the wheel cylinders 23. This continues until the annular piston 52 abuts the shoulder 50; whereupon continued rearward movement of the control member 4@ opens up its central opening 62, and

arcano? thereafter opens the exhaust port 74 to completely bleed pressure out of the wheel cylinders 2S, and the fluid dislacement chamber 48.

ln some instances it may be desirable to produce a larger reaction force upon the control member Kill and this can be easily accomplished by causing the end of the control member lll to abut the annular piston S2 prior to the time that the land 'lo allows pressure to be communicated to the control port 68. This is simply accomplished by extending the land portion 76 to the position shown by the dash-dot line gli. `Nith this arrangement, the annular piston 52 will be moved out of engagement with its shoulder d* prior to the time that pressure is communicated to the wheel cylinders 2,8, and the iluid displacing chamber 4S so that the reaction that is exerted upon the control member lo is that produced by the larger diameter of the annular piston 52. With this arrangement the control member all need not close off the exhaust port 74- prior to engagement with the annular piston 52. linmediately following separation of the annular piston 52 from the shoulder Si), the rear face 96 of the land le opens communication with the control port dll to actuate the brakes. With this construction very little pressure flow is required of the hydraulic pump lb inasmuch as some of the displacement is always delivered manually. Further advantage occurs by reason of this construction in that no lost motion is involved in the transition from pressure actuation to manual actuation; inasmuch as the annular piston S2 is being moved at all times, and the check valve structure Sil automatically closes when the manually developed pressure exceeds that supplied by the accumulator le. The operation of this embodiment is believed to be otherwise similar to that previously recited so that it will be readily apparent to those skilled in the art, and need not further be elaborated upon.

lt will be apparent that the objects heretofore enumerated as well as others have been accomplished; and that there has been provided a new and improved piston arrangement whereby a single fluid pressurizing cylinder provides both a reaction force, and a fluid displacement chamber which can be operated manually by the continued forward motion of the control member.

While the invention has been described in considerable detail, I do not wish to be limited to the particular construction shown and described; and it is my intention to cover hereby all novel adaptations, modifications and arrangements thereof which come within the practice of those skilled in the art to which the invention relates.

l claim:

l. ln a fluid pressure device: a housing having a forwardly and rearwardly extending lluid pressure chamber; a piston in said chamber; stop means preventing rearward movement of said piston beyond a retracted position; said housing having an exhaust port communicating with said chamber adjacent said piston; a control member having a normal position in said chamber rearwardly of said piston; said control member when in said normal position establishing communication between said exhaust port and said chamber forwardly of said piston, and closing off communication upon forward motion from said normal position, and thereafter moving said piston out of engagement with said stop means; said housing also having a pressure supply port, and a control port communicated by a passage with said chamber forwardly of said piston; and valve means which communicates said pressure port with said chamber forwardly of said piston upon forward movement of said control member after said piston moves out of engagement with said stop means.

2. In a fluid pressure device: a housing having a forwardly and rearwardly extending iluid pressure chamber; an annular piston in said chamber; stop means preventing rearward movement of said annular piston beyond a retracted position; said annular piston having a valve seat surrounding its central opening and facing in a rearward direction; said housing having an exhaust port communieating with said chamber rearwardly of said vaive seat; a control member having a normal position in said chamber rearwardly of said annu'iar piston; said control member establishing communication between said exhaust port and said valve seat in its normal position, and closing orf said valve seat upon forward motion from said normal position, and thereafter moving said annular piston out of engagement with said stop means; said housing aiso having a pressure supply port, and a control port which communicates with said chamber forwardly of said annular' piston; and valve means which communicates said pressure port with said chamber forwardly of said annular piston upon forward movement of said control member after said annular piston moves out of engagement with said stop means.

3. In a uid pressure device: a housing having a forwardly and rearwardly extending uid pressure chamber; an annular piston in said chamber; stop means preventing rearward movement of said annular piston beyond a retracted position; a control member having a normal position in said chamber rearwardly of said annular piston;

the portion of said chamber forwardly of said annular piston and said control member forming a iluid displacement chamber whose pressure exerts a rearward force on said annular piston and control member; said control member being adapted to abut and drive said annular piston forwardly; said housing having a control port communicating with said iiuid displacement chamber; means providing a pressure inlet port; means providing an exhaust port; and valve means normally communicating said exhaust port to said fluid displacement chamber in said normal position of said control member, said control member being operatively connected to said valve means to gradually close 01T said exhaust port and gradually open said pressure port to said fluid displacement chamber upon forward motion of said control member prior to its abutment with annular piston; whereby a small reaction is provided during normal valve control movement, and continued forward movement of said Control member causes said annular piston to displace uid from said chamber.

No references cited. 

1. IN A FLUID PRESSURE DEVICE: A HOUSING HAVING A FORWARDLY AND REARWARDLY EXTENDING FLUID PRESSURE CHAMBER; A PISTON IN SAID CHAMBER; STOP MEANS PREVENTING REARWARD MOVEMENT OF SAID PISTON BEYOND A RETRACTED POSITION; SAID HOUSING HAVING AN EXHAUST PORT COMMUNICATING WITH SAID CHAMBER ADJACENT SAID PISTON; A CONTROL MEMBER HAVING A NORMAL POSITION IN SAID CHAMBER REARWARDLY OF SAID PISTON; SAID CONTROL MEMBER WHEN IN SAID NORMAL POSITION ESTABLISHING COMMUNICATION BETWEEN SAID EXHAUST PORT AND SAID CHAMBER FORWARDLY OF SAID PISTON, AND CLOSING OFF COMMUNICATION UPON FORWARD MOTION FROM SAID NORMAL POSITION, AND THEREAFTER MOVING SAID PISTON OUT OF ENGAGEMENT WITH SAID STOP MEANS; SAID HOUSING ALSO HAVING A PRESSURE SUPPLY PORT, AND A CONTROL PORT COMMUNICATED BY A PASSAGE WITH SAID CHAMBER FORWARDLY OF SAID PISTON; AND VALVE MEANS WHICH COMMUNICATES SAID PRESSURE PORT WITH SAID CHAMBER FORWARDLY OF SAID PISTON UPON FORWARD MOVEMENT OF SAID CONTROL MEMBER AFTER SAID PISTON MOVES OUT OF ENGAGEMENT WITH SAID STOP MEANS. 